Grid-making machine



Nov. 28. 1939. H. M WASHBURN GRID-MAKING MACHINE 8 Sheets-Sheet 1Qriginal Filed Oct. 26, 1936 1 11 067750 2 HENRY M MsH'Bu/N bio 3776i?Nov. 28, 1939.

H. M. wAsHBuRN GRID-MAKING MACHINE Original Fi1 ed Oct. 26, 1936 y 8Sheets-Sheet 2 17106 1201 .figmy llMls/aau/w Nov. 28, 1939. H. M.WASHBURN GRID-MAKING MACHINE Original Filed 0ct.- 26, 1936 8 Sheets-Shet3 Si Hi Inventor HEN/er M MSl/BURN 2.1s1,2ss

Nov. 23, 1939.

H. M. WASHBURN GRID-MAKINGMACHINE s Sheets-Sheet 4 Original Filed Oct.26, 1936 Nov. 28, 1939. H. M. WASHBURN Gain-MAKING MACHINE OriginalFiled Oct. 26, 1936 8 Sheets-Sheet'S r .@N 0% WM IN W N H Nov, 28, 1939.

H. M. WASHBURN ham-MAKING MACHINE Olfiginal Filed 001;. 26, 1936 8Sheets-Sheet 6 Patented Nov. 28, 1939 PATENT GRID -.MAKING MACHINE HenryM. Washburn, Newtonville, Mass, assignor to Raytheon ProductionCorporation, Newton, Mass, a, corporation of Delaware ApplicationOctober 26, 1936, Serial No. 107,647

; Renewed April 21, 1939 27 Claims.

This invention relates to a novel grid-making machine adapted for themanufacture of the wound type-of grid electrode as used in radio tubesand other types of electrical space discharge devices.

An object of this invention is to devise a machine to produce woundgrids in which the side rods are perfectly straight as they come off themachine, and which are ready to be assembled in a tube without furthershaping or straightening.

Another object of my invention is to devise such a machine which isfully automatic, and which has a very large rate of output.

Other objects relate to the general improvement of the organization andarrangement of mechanisms of such a grid-making machine, including,among other novel mechanisms, an improved arrangement for feeding thegrids through the machine and for severing completed grids, a novelarrangement for changing the driving speed so as to control the pitchand number of turns in the completed grids, a novel arrangement forsupporting a rotating wire-carrying spool in dynamic balance, and anovel arrangement for enabling the machine to produce right and lefthandwound grids.

The foregoing and other objects of my invention will be best understoodfrom the following description of an exemplification thereof, referencebeing had to the accompanying drawings,

wherein:

Fig. 1 is a front elevation of the machine; Fig. 2 is a section alongline 22 of Fig. 1,

showing the drive of the back shaft;

Fig. 3 is a section taken along line 3-3 of Fig. 1, showing the cammechanism for the cutter knives, swedges, and grid-straighteninghammers;

Fig. 4 is a section taken along line 4-4 of Fig. 3, showing theclutch-actuating mechanismfor disengaging the cutter mechanism duringthe movement of the leg portion of the grid past the cutter position;

Fig. 5 is a plan view of the machine;

- Fig. 6 is a section taken along line 66 of Fig. 1, showing the windinghead drive and part of the cutter-actuating mechanism;

Fig. 7 is a section taken along line of Fig.

1, showing the face of the winding head and the stripper timing switch;

Fig. 8 is an enlarged section taken along line 8-8 of Fig. 5, showingthe construction of the winding head and-of the swedge mechanism unit;

g. 9 is a section taken along line 9-9 of Fig.

8, showing the cutter-actuating rocker arms and.

the grid arbor chuck;

Fig. 10 is a section taken along line Ill -i0 of Fig. 8, showing theface of the winding head;

Fig. 11 is a transverse section taken along line 5 llli of Fig. 8,showing the mechanism involving the cutter knives, the swedges, and theactuating hammers in relation to the grid and its associated arbor;

Fig. 12 is a back elevation of the machine; 19 i Fig. 13 is a'sectiontaken along line l3-l3 of Fig. 1, showing the swedge mechanism unit;

Fig. 14 is a section taken along line M-M of Fig. 13, showing theadjustable swedge support;

Fig. 15 is a section taken along line I5-l5 of 15 Fig. 1, showing thelock and release mechanism for moving the swedge mechanism unit out ofposition for replacement of the. winding wire spool;

Fig. 16 is a section taken along line l6-'I6 of Fig. 1, showing therelationship of the various shafts mounted in the bearing plate at thefront end of the pull-out feed unit;

Fig. 17 is an enlarged section taken along line l'iI|- of Fig. 1,showing one face of the front 25 pull-out feed carriage carrying thestripper mechanism;

Fig. 18 is .a section taken along line l8 -I8 of Fig. 17, showingfurther details of the associated mechanism; 30

Fig. 19 is an enlarged section taken along line l9-|9 of Fig. 1, showingthe other face of the front pull-out feed carriage;

Fig. 20 is an enlarged section taken along line 2020 of Fig. 1, showingone face of the back 35 pull-out feed carriage;

Fig. 21 is a section taken along line 2I-2l of Fig. 20, showing furtherdetails of the associated 'mechanism;

Fig. 22 is an enlarged section taken along line 4 2222 of Fig. 1,showing the other face of the back pull-out carriage;

. Fig. 23 is an end view of the machine partly broken away, viewing themachine from the right Fig. 27 is a section taken along line 21-21 ofFig. 26;

Fig. 28 is an enlarged view of the grid arbor and the associatedcutters, swedges, and gridstraightening hammers illustrating theformation of the grid;

Fig. 29 is a section along line 29-29 of Fig. 28; Fig. 30 is a completedgrid substantially full size;

Fig.31 is an enlarged view of a swedged-joint between a grid turn andone of the side rods Fig. 32 is a plan section on line 32-32 of Fig. 1;

Fi 33 is a perspective view of the skip mechanism actuated during thewinding of the loose turns on the grid;

Fig. 34 is an enlarged view of the winding wire lead-in plates;

Fig. 35 is a side view of the winding wire leadin plates;

Figs. 36 and 37 are two views of grids illustrating defects which tendto occur in, wound grids and which are eliminated by the presentmachine;

Fig. 38 is an enlarged view showing the relationship between the arbor,one of the side rods of the grid, and its associated swedge; and

Fig. 39 is a wiring diagram of the stripping mechanism.

The usual method of making wound grids at the present time is to cut aseries of grooves in a pair of side wires, to wind a winding wire inthese grooves, and to swedge the grooves over the winding wire. Gridsmade on the usual gridmaking machine inevitably are produced withdistorted side rods so that a subsequent straightening process isnecessary. This straightening process usually consists of hotstretching" the grids by heating the side rods to a relatively hightemperature and giving them a slight stretch so as to straighten themout. This hot stretching produces an oxide coating on the grids, andtends .to bake other impurities thereon, which -oxides and impuritiesmust be removed by hydrogen baking. This is not only expensive butunsatisfactory from various standpoints.

I have found that in machines which operate with relative rotationbetween the arbor on which the grid is formed and the swedging andcutting members, the side rods are given a twist or bow longitudinallywhich results in a curve of the side rods out of the plane of the grid,as illustrated in Fig. 36, which shows a completed grid viewed edgewise.I have found that the tendency for this type of distortion can besubstantially eliminated by eliminating the relative rotation betweenthe arbor and the cutting and swedging members, and causing the cuttingand swedging members to contact with the side rods at the center thereofalong the axis of the grid.

The elimination of the tendency to curve out of the plane of the gridstill leaves a tendency for the side rods to curve in the plane of thegrid, as illustrated in Fig. 37. This is probably due to the stretchingof one side of the siderod during the cutting and swedging. I haveprovided mechanisms whereby this distortion of the side rods is alsoeliminated.

In the drawings, 3| designates the bed plate of the machine which issupported by the bed plate supports 32 and 33. On the bed plate 3| ismounted the two winding head-supporting standards 34 and 35. In thesestandards is mounted a support tube which is held stationary withrespect to said support standards. 0n

the outer end of the support tube 36 is mounted a support block '31which carries two brackets 38 and 39.- These brackets rotatably carry apair of reels 40 and 4| from which are fed the side rod wires 42 and 43.

Arb r structure In the inner end of the support tube 36 is mounted thearbor 44 upon which the grid is formed. The arbor 44 has a shank 45which fits tightly into an adapter 46, whereby the arbor is rigidlycarried by said adapter. The arbor and its adapter are clamped in thesupport tube 36 by a split V-block 41. This split V-block is forcedagainst" the adapter 46 by means of a set screw 49 which bears againstthe V-block base plate 48.

The set screw 49 is mounted in the main head 62 which is likewisecarried by the support tube 36. The arbor 44 is provided with a pair ofside grooves 50 in which the side rod wires 42 and 43 lie and throughwhich they are fed into the gridforming position. As will be seen fromFigs. .8 and 11, the inner ends of the arbor 44 and the arbor shank 45are tapered so as to facilitate the threading of the side rod wires 42and 43 into the grooves 50. The arbor 44 is slightly tapered so as todecrease in thickness toward its outer end. Since the minor diameter ofthe grid which is formed depends upon the thickness of the arbor in thegrid-forming position, very fine adjustments in the exact diameter ofthe grid-can be secured by moving the arbor longitudinally in thesupport tube 36. The clamping arrangement-afiorded by the members 41, 48and 49 permit this adjustment to be made. Of course it is to beunderstood that the substantial size of the grid is determined in eachcase by the size of the arbor which is readily removable from. thesupport tube 36 so that various sizes of arbors can readily be used.

Cutter mechanism Mounted at the sides of the arbor 44 are the twocutters 5|. The cutters are carried by hubs 52 which are received in hubblocks 53. The hubs 52 and consequently the cutters 5| are rotatablyretained in the hub blocks 53 by means of a ballbearing backed by aspring and plug, as indicated at 54. The cutter hub blocks 53 areslidably mounted in the cutter slide carriage 55, whereby their positionin said cutter slide carriage can be adjusted. The cutters are aflixedin their adjusted position by means of set screws 56. The cutter slidecarriage is slidablysupported in the main head 62 by means of gibs 51retained in place against the front face of the main head 62 by means ofcover blocks 58.- In order to limit the motion of the cutter slidecarriage 55, this carriage is provided with a pair of stops 60 betweenwhich is arranged a stop 59 which is formed as part of the lower coverblock 58. The

cover blocks 58 are retained in place on the main head 62 by means ofscrews 6|.

Due to the above support arrangement, the two cutters 5| are adapted toslide as a unit back and forth in the plane of the grid, that is, in theplane in which the grooves 50 lie. In order to reciprocate the cutters5|, a pair of rocker arms 64 push against two projections 63 formed onthe back of the cutter slide carriage 55. The rocker arms 64 are mountedon the ends of two rocker arm shafts 65, which in turn are rotatablymounted in the main head 62. The rocker arm. shafts 65 project throughthe main head 62, and carry at the opposite ends thereof the two backlink-actuating arm 69 in the forward position,

a takeup spring 68 is provided on each rocker arm link 61. Eachlink-actuating arm 69 is mounted on a cutter-actuating shaft 10. shownin Fig. 3, each cutter-actuating shaft 16 is driven by means of acutter-actuating arm 1| mounted thereon. Each cutter actuating arm 3|drives its respective cutter-actuating shaft through an intermittentclutch mechanism, which will be described below. The cutter-actuatingarms 1| are in turn driven by a cutteractuating cam 12, as shown in Fig.3. The cutteractuating cam 12 is rigidly carried by a cambearing sleeve13 onto which it is pressed tight. The cam-bearing sleeve 13 isrotatably mounted on the support tube 36. In order to drive thecutter-actuating cam 12, the cam-bearing sleeve has also pressed thereona cam drive gear 14. As shown in Fig. 1, the gear 14 is in turn drivenby a gear 15 which is mounted on the drive shaft 15 journaled in thesupport standards 34 and 35. The drive shaft 16 is driven fromsomesuitable source of motive power through a drive pulley 11 and drivebelt 18.

Upon rotation of the drive shaft 16, the cutteractuating cam 12 isrotated through the gears 15 and 14, respectively. The cam 12 isprovided at diametrically opposite points with a projection and adepression. Therefore, upon rotation of the cam 12, the cutter-actuatingarms H are rocked back and forth once during each complete revolution ofthe cam 12. This in turn oscillates the slide carriage rocker arms 64through the intermediary of the linkage, as shown on Fig. 6. Theoscillation of the rocker arms 64 acting upon the projections 63likewise oscillates the cutter slide carriage 55 carrying the cuttersSince the rocker arm links 61 are driven by the link-actuating arms 69through the intermediary of the takeup springs 58, any tendency of the'cam 12 to over-drive the slide carriage is taken up by thepin-and-s'lot connection between the link-actuating arms 69 and therocker arm links 61. This takeup is necessary since the travel of thecutter slide carriage 55 is limited by the stops 59 and 66. Upon thereciprocation of the cutters 5|, as described above, the cutters willcut notches 95 in the two side wires 42 and 43, as illustrated clearlyin Fig. 28.

In order to compensate for different widths of arbors and to adjust fordifferent depths of notches 95, the set screws 56 maybe released and theposition of the cutter hub blocks 53 adjusted by means of adjustingscrews 56, illustrated in Figs. and 11. The cutters are then retained intheir adjusted down on the set screws 56. 7

Each grid which is formed contains a definite number of turns of wirewhich is rigidly connected by a swedging operation to the side wires 42and 43. After the winding of a grid has been completed,'it is desirablethat a few loose turns be wound around the side wires'42 and 43 beforethe succeeding grid is formed. The portion of the grid upon which theseloose turns are wound is called the leg portion. During the travel ofthe leg portion of the grid past the cutters, it is desirable that thecutters shall be idle. In order to accomplish this I have proposition bytightening vided the cutters withv an intermittent drive mechanism,which includes the clutch arrangement between the cutter-actuating arm1| and the cutter-actuating shaft 10, as mentioned above. This clutcharrangement is shown most clearly in Figs. 3 and 4. Eachcutter-actuating arm 1| is mounted upon a hub 19, which in turn isprovided with a recess 80 into which a tongue 8| of the sleeve 82 isadapted to be received. The sleeve 82 is rotatably mounted on thecutteractuating shaft 18, and is driven therefrom by means of' a sleeve86 pinned onto the shaft 10. The sleeve 82 is provided with an elongatedtongue 84 which fits into an elongated slot 85 in the sleeve 86. Byshifting the sleeve 82 to the left in Fig. 4, the tongue 8| may be movedout of the recess 80, thus disconnecting the shaft 10 from thecutter-actuating arm 1|. In order to accomplish the shifting of thesleeve 82, it is provided with a circumferential groove 83 into whichfit a pair of pins carried by a clutch throw-out lever arm 81 carried bythe cross-shaft 88. This cross-shaft is mounted in bearings 89 carriedby the base plate 3|. The cross-shaft 88 is rocked 'by means of a camarm 96 cooperating with a clutch throw-out cam 9| driven from the maincam shaft 92. The driving mechanism for this cam shaft constitutes aspecial feature of this invention, and will be described below. As shownmost clearly in. Fig. 5, the cam 9| is provided with a raised portionwhich pushes against the arm 90 once during each revolution of the maincam shaft 92, and thus disengages each cutteractuating shaft 18 from itsrespective cutteractuating arm 1|. During the time of thisdisengagement, the cutters are inactive and do not form any notches 95.The cam 9| is so disposed on the main cam shaft 92 that thisdisengagement occurs during the passage of the leg portion of the gridpast the cutters. The cam 9|, as indicated in Fig. 3, is adjustable sothat the initiation of the inactive period of the cutters and theduration of this inactive period can be varied at will. i

In order to avoid excessive wear and replacement of the cutters 5|, Iprovide each cutter in circular form with a continuous cutting edgearound its periphery. I also provide means for continuously rotating thecutters so as to provide a new cutting edge to the side wires 42 and 43for each successive notch 95. As shown in Fig. 7, this mechanismconsists oftwo cutterrotating fingers 93 which are pivoted at one end tothe upper cover block 58 and urged toward the cutters by means of a biasspring 94. Each cutter-rotating. finger 93 against the edge of a cutter5| at a point slightly inside of the center. As the cutters arereciprocated back and forth underneath the fingers 93, apawl-and-ratchet effect is produced which gives to each cutter 5| aseries of thrusts which produces a slight rotation of each cutterbetween each cutting operation.

Winding mechanism I ,After the notches 95 have been cut into the siderod wires 42 and 43, a winding wire 96 is laid into these notches andwound around the side wires 42 and 43 so as to form the grid. In

.order to guide' the winding wire 96 into the frictionally bears aredisposed around the arbor 44, as shown most clearly in Figs. 34 and 35.The winding. wire 96 is fed from a winding wire spool 98 over pulleys 99carried by a pulley arm I06 mounted on the winding head I04. In orderthat the winding wire spool 98 be dynamically balanced, it is mountedconcentrically with its axis of rotation upon three 'spool support pinsI00 carried in the spool support ring IOI, as shown in. Fig. 8. Thespool .support ring is rotatably mounted on three rollers I02 which arereceived in a pcripheral groove around the edge of the spool supportring, as shown in Figs. '7. and 8. The rollers I02 are in turn carriedby the winding head I04. In order to place the proper tension upon thewinding wire 96 as it is laid into the notches 95, there is provided aspool brake I03 which is likewise carried by the winding head I04. Thespool brake engages the peripheral groove in the spool support ring I0|. The pressure with which said brake bears upon the spool ring may beadjusted by the spring-and-screw adjustment I05.

In order to drive the: winding head I04, thereis formed integraltherewith a gear I01. The winding head itself is rotatably mounted uponthe main head 62 through the intermediary of ball bearings I08. Oneseries of the ball bearings I08 is received in the ball race I09 formedon the main head 62. Another series of the ball bearings I08 is receivedin a ball race ring IIO which is adjustable along the main head 62. Theball race ring IIO may be locked in position by means of the lock nutIII. The gear I0! is driven by a gear II2 mounted on the drive shaft I6.

Upon rotation of the drive shaft 16, the winding head I04 is driventhrough the intermediary of the gears H2 and I01. The winding headthereupon carries the pulley arm I06 around so as to wind the windingwire 96 around the side rods 42 and 43 and into the notches 95. The pullexerted by the winding wire 96 upon the winding wire spool 98 causessaid winding wire spool, together with the spool support ring, to rotatein the rollers I02. As pointed out above, the proper tension ismaintained -on the winding wire 96 by means of the brake I03.

Since' the winding wire spool 98 is mounted concentrically with its axisof rotation, it is at all times in dynamic balance independent of theamount of wire which it carries. Therefore, winding wire spools havinglarge amounts of wire can be placed upon the machine without anyinconvenience whatsoever, and thus decrease the idle time of the machinewhich arises from the necessity of replenishing the winding wire.

swedge mechanism After the winding wire 96 is placed in the notches 95,the notches are swedged around the winding wire 96 so as to rigidly fixthe winding wire in the side rods 42 and 43. Thisswedging is illustratedin Figs. 28 and 31. In order to accomplish this swedging, I provide themachine with two swedges II3 on oppositesides of the arbor 44. As shownin Fig. 11, each swedge H3 is carried by a swedge hub II4 which isreceived in a swedge hub block II5. These swedges are rotatably retainedin the swedge hub block II5 by means of an arrangement II6, consistingof a ball bearing backed by a spring and plug. The swedge hub blocks II5areslidably mounted in the swedge slide blocks I I1. By adjusting theposition of the swedge hub block H5 in the swedge slide block I I1, acoarse adjustment of the depth of the swedging operation is obtained.The swedge hub blocks II6 are retained in their adjusted position bymeans of set screws II8, as shown in Fig. 14. The swedge slide blocksare in turn slidably mounted in support blocks II9 which in turn arecarried by the swedge assembly carriage I46 through an adjustableconnection which will be described below.

Between the support blocks H9 and the slide 1 blocks III is provided anadjustable bearing I20 so that any wear in the bearing is readilycompensated for, whereby the swedges are maintained accurately in theirdesired operating position.

In order to slide the blocks I I1 within the sup- 1 port blocks II 9 soas to bring the swedges II3 into contact with the side wires 42 and 43,and thus produce the swedging action referred to above, I provide theslide blocks II! with projections I2I, as shown in Figs. 11 and 13. Each2 the carrier arm I23 which in turn provides for a 3 depth adjustmentfor each swedge and also for the hammer mechanism which will bedescribed below. The actuating arm I25 has pivoted thereto a link I21which connects it to an oscillating arm I28 pivoted approximately at itsmidpoint on' the swedge assembly support standard 282. The oscillatingarm is extended at one end thereof, which end has pivoted thereto aconnecting link I29 which is connected in turn to the rocker arm I30.The rocker arm I30 is carried on a 4 rocker arm shaft I33 journaled inthe standards 34 and 35. Said rocker arm I30 is free to rotate aroundsaid rocker arm shaft. The rocker arm is driven through a driving armI3I which is carried by the rocker arm shaft I33 and moves 4 therewith.The driving connection between the driving arm I3I and the rocker armI30 is provided by means of an adjustable driving pin I32. Since therocker arm I30 drives both impact arms I22, an adjustment of the drivingpin I32 5 provides a simultaneous depth adjustment of both swedges andboth hammer mechanisms. The rocker arm shaft I33 is oscillated by meansof the swedge-actuating cam I35, as shown in Fig. 3. The drivingconnection between the cam 5 I35 and the shaft I33 is afforded by meansof the swedge-actuating arm I34 rigidly connected to 'the shaft I33. Thecam I35 is provided with a projection which by reacting upon the arm I34oscillates the shaft I33 once during each revolu- 0 tion of said cam.The cam I35 is rigidly mounted upon the cam bearing sleeve 13 which, asdescribed above, is driven by the gears I4 and I5 from the driving shaft16, and thus is synchronized with the winding head I04. I! When the camI35 is rotated, as described above, and the arm I33 is oscillated, eachimpact arm I 22 deals a blow to the respective projections I2I, which inturn slide the swedge slide blocks I I1 carrying the swedges II3intoward 7 the side rods 42 and 43, thus causing the swedges I I3 toimpart to the side rods 42 and 43 a swedging blow which swedges the siderods around the winding wire, as indicated in Fig. 28. Since both impactarms I22 are driven simultaneously by 1 Pivoted upon each 2 the samedriving mechanism, the swedges likewise move simultaneously in towardthe side rods and deliver their swedging blows on opposite sides of thearbor 44 at the same instant. Thus the thrusts upon the opposite sidesof the arbor Ill and bearing against a plate I3I fastened tothe swedgeslide support block H9.

In order to deactivate the swedges during the passage of the legportions of the grids past the swedging position, each impact arm I22 isprovided with a recess I38, and means are provided for raising eachimpact arm I 22 so as to bring said recess I38 opposite its respectiveprojection l2I. Thus when the impact arms I22 are oscillated in theirraised position, each projection I2I is received in a recess I38, and noimpact blow is delivered thereto. Thus the swedges under theseconditions are not actuated. In order to raise each impact arm I22, alink I39 is provided with an-elongated slot through which passes a pinwhich is rigidly connected to the lower end of the arm I22. Each carrierarm I23 is likewise provided with elongated slots through which the pinsconnected to the impact arm I22 pass so as to permit a sliding movementof the impact arm I 22 in said carrier arm I23. Each link I39 is pivotedat its lower end to a fulcrum block I40 carried by the bed plate 3I.Each link I 39 likewise has pivoted to it at an intermediate point anactuating link I4I, which in turn is pivoted at its lower end to anactuating lever I42. Each actuating lever is pivoted at an intermediatepoint thereon to a pivot block I43 carried by the lower face of the bedplate 3I.' Of course the bed Plate 3I is provided with openings, notshown, through which the actuating links I4I can project. The actuatinglevers I42 are driven by a swedge throw-out cam I44 which in turn isrigidly carried by the main cam shaft 92.

Upon rotation of the cam shaft 92 and the 'cam I44, the outer end ofeach actuating lever I42 is depressed when the raised portion of the camI44 comes into contact therewith. Through the linkage described above,the outer end of each link I39 is raised, and thus each impact arm I 22is likewise raised. In this manner the swedges are deactivated duringthe passage of the leg portion of the grid past the swedging position.As shown in Fig. 13, the cam H4 is adjustable so that the initiation ofthe'inactive period of the swedges and the duration of said inactiveperiod may be varied at will. The slot-and-pin arrangements describedabove and shown most clearly in Fig. 13 permit the oscillation of thecarrier arms I23 and the impact arms I22, in either the raised orlowered position of the links I39. After the raised portion of the camI44 has traveled beyond the levers I42, each impact arm I22 is returnedto its lower or active position by means of a spring I45.

As described above, the operating points on both the swedges and thecutters are oscillated in the plane passing through the centers of theside rods 42 and 43, and likewise strike the side rods at points lyingin this plane. As described above, this arrangement substantiallyeliminates the tendency for the side rods to be distorted in the manneras indicated in 36. However, due

to inequalities in the arbor grooves, inequalities in the size of theside rods, wearing of the arbor grooves, and various other more or lessobscure reasons, some tendency usually remains for the side rods to bebowed, as shown in Fig. 36. I have found that these slight residualtendencies can be compensatet for by adjustments of the swedges II3. Inorder to illustrate this action, reference may be had to Fig. 38.Theoretically the swedge I I3 is reciprocated along the line of thearrow d, and impacts one of the side rods 42 at the center thereof,indicated at the point a. If the side rod 42 asit comes from the machineis bowed in such a direction as to be concave at the left and convex atthe right, I have found that if the swedge I I3 is shifted laterally inthe direction toward the point D, the distortion can be eliminated andthe side rod 42 will come off the machine perfectly straight Likewiseifthe side rod 42 comes oif the machine with a concavity at the.

right and a convexity at the left of Fig. 38, shifting of the swedge II3laterally to the left will eliminate this distortion. In shifting theswedge II3 laterally in either direction, its motion of travel duringoperation along the direction of the line dis undisturbed. The shiftingmerely causes the swedge to bear more heavily on one side or the otherof the side rod 42, and thus compensate for the tendency to produce thedistortions described.

The adjustment of the swedges H3, as described above, is accomplished inmy machine by vertically adjusting the position of said swedges. Asshown in Fig. 14, the swedge support blocks II9' are adjustablysupported on the swedge assembly carriage I 46. The support block H9 isretained in place on said carriage I46 by means of screws I41 passingthrough elongated holes I49 There is provided a further adjustment sothatv the swedges may be adjusted laterally along the arbor 44 in orderto bring the swedges exactly opposite the notches 95during the swedgingaction. In order to accomplish this lateral adjustment, each swedgeassembly carriage I46 is adjustably mounted upon the swedge assemblyframe I50, as shown" in Figs. 8 and 11. Each swedge assembly carriageI45 is also provided with a block I53 into which is tapped a microme-iter adjustment screw II. Each micrometer adjustment screw is in turnrotatably carried bya yoke I52 mounted upon the swedge assembly frameI50. By rotating the micrometer adjustment screw I5I, the position ofeach of the swedges II3 laterally in the machine can be adjusted verygradually. The swedge assembly car-.

riage is firmly retained in this adjusted position by means of hold-downscrews I54 whichpass through elongated slots in the swedge assemblycarriage I46, and are tapped into the swedge assembly frame I 50.

The construction as described above, together with the adjustmentstherefor, eliminates the type of distortion as illustrated in Fig. 36.However, as stated above, a tendency still exists for the side rods tobe bowed in the plane lying along the centers of the side rods, asillustrated in Fig. 37. I have found that if there is provided, as shownin Fig. 28, hammers I55 which strike the side rods 42 and 43simultaneously with the swedges II3, the tendency for the distortion asillustrated in Fig. 37 is eliminated.- This effect produced by thehammers I55 is probably due to two reasons. First, the hammersmayactually bend the side rods 42 and 43 back into a straight conditionafter they have been bent out of this condition by-the action of thecutters 5I and the swedges II3. Second, by holding the side rods firmlyin contact withthe arbor 44 during the time the swedging action. takesplace, the side rods maybe held in their straight condition and beprevented from being bent out of that position by the swedges H3.

As shown in Fig. 11, the hammers I55 are adiustably mounted upon hammerhubs I56, which in turn are carried and pivoted upon the swedge assemblycarriage I46. The hammers I55 are retained on thehubs I56 by means ofscrews I'51 which pass. through enlarged holes in the hammers I55, andare tapped into the hammer hubs I56. This permits the hammers to beadjusted both laterally and vertically for purposes to be describedbelow. The hammers are actuated by hammer-actuating slides I581 whichare retained in place on the swedge assembly carriages I46 by means ofthe cover plates I48. These hammeractuating slides are free to slidetransversely in the swedge assembly carriages I46. The outer end of eachhammer-actuating slide I58 is bent over to provide a portion which isadapted to be engaged bythe adjustable hammer-actuating pins I59. Thesehammer-actuating pins I59 are carried by the carrier arms I23. Asdescribed above in connection with the actuation of the swedges N3, thecarrier arms I23 are constantly rocked back and forth by a linkageconnected with the rocker arm shaft I33. As each carrier arm I23 isrocked back and forth, the pin I59 strikes the end of thehammer-actuating slide I58, and thus pushes the hammer I55 intoenagement with the side rods 42 and 43. As the pins I59 leave the slidesI58, the hammers I55 and the slides I58 are pulled away from the arbor44 by the springs I60. Since each pin I 59-is independently adjustable,the intensity of the stroke of each hammer can be independently varied.

I have found that if all the curvature is not taken out of the side rodsby means of the adjustment of the swedges II3, any slight residualcurvature may be entirely eliminated by adjustmg the hammers I55 whichhave a convex impact surface, both laterally and vertically, along theside rods 42, which acts to eliminate said curvature in the same manneras indicated for the swedges H3 in Fig. 38. Such adjustment, as pointedout above, is provided by the screw and enlarged hole arrangementbetween the hammers I55 and the hammer hubs I56.

By proper adjustment of the swedges and hammers in the mechanism which Ihave described above, the completed grids which leave the arbor 44 areperfectly straight, and when ejected from the machine are ready to beassembled in tubes without any, further straightening action.

Pull -out feed mechanism In my machine I have provided a novelarrangement for feeding the grids through the machine so as to make theaction of the machine entirely automatic. This feed mechanism comprisestwo pull-out feed carriages I 6I and I81 have mounted thereon a plateI82.

which alternately engage the side rods 42 and 43 with the winding wirewound thereon, and pull the grid structure through the machine in themanner as will be described below.

The front pull-out feed carriage I6I includes a carriage frame I62 whichis mounted upon outer bearing sleeves I14. Each outer bearing sleeve I14is in turn slidably mounted upon an inner bearing sleeve I15, which inturn is slidably mounted upon a bearing rod I16 carried by the front andrear-bearing plates I11 and I18. One of the outer bearing sleeves I14carries a cam portion I19, as shown in Fig. 33. The inner bearing sleeveI15 associated therewith carries a cam portion I80. Intermediate the twocam portions 119 and I is located a spreading member I8I.. Thisspreading member is rotatably mounted upon the exterior of said innerbearing sleeve I15. The spreading member I8I when actuated produces askip action which will be described below. However, the spreading memberI8I in the position as indicated in Fig. 18, merely acts as anintermediate thrust member between the'inner and outer bearing sleevesI15 and I14. Thus as the inner bearing sleeve I16 is moved along to theright in Fig. 18, the outer bearing sleeve I14 is likewise pushed alongto the right, and thus the front pull-out feed carriage IN is moved inthe proper direction for feeding the grids .through the machine.

In order to produce the feeding mdvement of the inner bearing sleevesI15, said bearing sleeves The plate I82 carries a split nut I63 pivotedat one end thereof to the plate I82, as shown in Fig. 17. A biasingspring I64 connected to the other end of the split nut I63 biases thetwo halves thereof so as to clamp the lead screw I65. The drive of thislead screw also constitutes a novel feature of my invention, and willfurther be described below. Thus, when the lead screw I65 is rotated,the split nut I63 will be carried forward along said lead screw, andthis in turn will move the front pull-out feed carriage in aforward-direction to feed the grids through the machine.

In order for the front pull-out feed carriage to engage the grids, it isprovided with a pair of clamp slides I68 which are supported so as toslide vertically on the front carriage frame I62, as indicated in Fig.19. In order to actuate the clamp slides, a clamp slide lever I61 ispivoted at one end to each of said clamp slides I66. The other endofeach of the clamp slide levers I61 is pivoted on the front pull-outcarriage frame I62. Each lever I61 has pivoted at an intermediate pointthereon a link I66, which in turn is pivoted to a bell crank I69 carriedby and adapted to rotate on the front carriage frame I62. The

bell crank I69 is provided with an arm I10 and is actuated by means of acam rocker arm "I mounted upon a rod I83 carried by the front and rearbearing plates I11 and I18. Since the carriage I6I travels along themachine and the rocker arm IN is stationary, said rocker arm is providedwith an extension face 2I0 extending along the machine, as shown in Fig.5. The outer end of the arm I10 is provided with a roller which permitseasy motion along the extension face 2I0. The extension face 2I0 iscarried by -an arm which likewise is mounted upon the rod I83. In orderto provide for different thicknesses of wire, for wear on the cam slidesI66, and for adjustment of the clamping action, an adjustment thrust pinI12 is provided between the rockerarm HI and the arm carrying theextension face 2). The rocker arm "I is actuated by means of a riser camI13 mounted upon the main cam shaft 92, as shown in Fig. 17. As the camshaft 92 revolves in the direction as indicated by the arrow and the endof the rocker arm IN is pushed up by the raised portion of the cam, asshown, the arm I10 of the bell crank lever will be rotatedso as to causethe clamp slides I66 to clamp the grid between them. In this way thegrids are effectively clamped by the front pullout feed carriage IBI,and are carried along by the carriage I8I as it.travels forward alongthe machine. Thus, during the forward travel of the front feed carriageI 6| the grids are advanced through the machine. The clamping action ofthe clamp slides I66 is so adjusted that the clamping takes place on aleg portion of the grid.

Thus any distortion which occurs on the winding wire 96 does not injurethe grids inasmuch as this portion of the winding wire is later strippedfrom the grid and is discarded. As the cam shaft rotates further, therocker arm I1I drops from the raised portion of the cam I13, and aretracting spring I91 pulls upon the arm I18 of the bell crank, and thusrotates the bell crank so as to pullthe clamp slides I68 away from thegrid and thus release the grid. As will be described below, just priorto this release, theback pull-out feed carriage will have engaged thegrid and will continue the feed action thereof through the machine.

As indicated in Fig. 39, between the tight or normal turns 241 of thegrid there are wound a few loose turns 249 on the leg portion of thegrid.

Since the loose turns 249 are subsequentlyv stripped off and thrownaway, the wire of these loose turns is wasted. Therefore it is desirableto increase the pitch of the turns 249 so as to waste as little Wire aspossible. In order to produce this action, the grids are advancedthrough the machine at a more rapid rate during the time that the looseturns 249 are wound on the side wires 42 and 43. This increased rate offeeding is produced bythe skip mechanism to which I have referredbriefly above. This skip mechanism includes the spreading member I8Ibetween the two cam portions I19 and I88 on the two bearing sleeves I14and I15, as shown, for example, in Fig. 33. During a part of the timewhen the front feed carriage IGI is feeding the grids through themachine, the spreading member I8I is rotated so as to quickly separatethe front carriage frame I62 from the plate I82. The spreading member I8| is actuated during this time by means of a pull rod I84. Theactuation of the pull rod I 84 is produced by means of a tension springI85 which tends to pull upon the pull rod I84 and rotate the spreadingmember I8I so as to produce the skip action described. The action of thespring I85 is restrained by means of a cam I86 mounted upon the main camshaft 92. As the cam I86 rotates in the direction as indicated by thearrow in Fig. 19, the end of the pull rod I84 drops from the raisedportion of the cam to the depressed portion thereof, whereupon thespring I85 exerts its tension upon the pull rod I 84, and thus rotatesthe spreading member I8I so that it quickly separates the two camportions I19 and I88, and thus rapidly advances the front carriage frameI 62 along the machine. Due to.

this action, the rate of feeding of the grid through the machine isincreased, and thus the pitch of the wire 96 wound on the side rods 42and 43 is increased.

The length of the leg portion of the grid can be adjusted by adjustingthe distance which the spreading member I8I advances the frame I62. Thisdistance can be adjusted by adjusting the amount of rotation of thespreading member I8I. As will be seen from Figs. 18 and 33, the furtherthe member I8I is rotated the farther apart the cam surfaces I19 and I80will be forced which in turn determines the skip travel of the frameI62.

In order to provide this adjustment, the depressed portion of the camI86 is set sufficiently deep toprovide for the maximum travel of thepull rod I84 and consequently of the spreading member I8I. The pull rodI84 is usually stopped beforeit reaches the bottom of 'the depressedportion of the cam I86 by the stop 295 cooperating with the adjustablescrew 296. The stop is mounted on the pull rod I84 and the screw istapped into a block carried by the bed plate 3|, as shown in Fig. 19. Byadjusting the screw 296, the amountwhich the pull rod I84 travels underthe action of spring I85 may be adjusted. In this way the rotation ofthe spreading member I8I and consequentlythe length of the leg portionof the grid can be adjusted.

The cam I 86 isso arranged that the rotation of the spreading member I8Ioccurs during the passage of the leg portion of the grid past the winding po'sitionl The spreading action, as described above, occurs onlyduringthe time that the pull rod I84 drops from the raised to thedepressed portion of the cam I88. Subsequent to this action, the plateI82 will cause the front carriage frame I62 to be moved along themachine at the normal rate. After the back feed carriage has takencontrol of the feeding of the grids and the clamp slides have releasedthe grid, the cam I 86 pushes upon the rod I84 and moves it into theposition as shown in Fig. 19, during which time the spring I85 is putunder a tension so as to be ready for its next spreading operation. Atthis time the spreading member I8I is returned to its position, as shownin Fig. 18, by means of a retracting spring 288, as shown in Fig. 17.Upon return of the spreading member I8I to the position as shown in Fig.18, the front carriage frame I62 is pulled back toward the plate I82 bymeans of a tension spring 294, as shown in Fig. 33. This reestablishestherelationship between the front carriage frame I62 and the plate I82,as'shown inFig. 18. The pull rod I84 is slidably retained on the baseplate 3I while the front feed carriage carrying the spreading member I8Imoves along the machine with respect thereto. In order to permit thisrelative motion and still maintain the operative relationship betweenthe pull rod I84 and the spreading member I8I, said pull rod is providedwith an extension. face 289, which extends along the machine asufficient distance to be maintained in operative relationship to thespreader member I 8| which is provided with a roller at its outer end soas to permit easy motion along the extension face 289. The'return of thefront carriage frame I62 to its original position will be describedbelow.

The back feed carriage I81 which takes control of the feeding'of thegrids through the machine clampthe lead screw I65, whereby the back feedcarriage is advanced along the machine." The back feed carriage is alsoprovided with clamp slides I9I slidably mounted upon the frame I88, asshown in Fig. 22. The edge of the lower clamp slide I9I is sharpened toproduce a cutting edge. In this way the clamp slides I9I constitute notonly a clamp but also a cutter which severs the grids after they havebeen completed and are ready to be ejected from the machine. The clampslides are actuated by means of levers I92 which are pivoted at one endto the slides I9I and at the other end to the frame I88. Intermediatethe ends of the levers I92 are pivoted connecting links I93 which inturn are pivotally connected to a bell crank I94. The bell crank I94 issupported upon and adapted to rotate in the frame I88. The bell crankI94 is provided with an arm I95. The arm I95 is actuated to cause theclamp slides I9] to engage the grid by means of a cam rocker arm I98,which drives an actuating arm 292 through an adjustable driving pin I99, whereby adjustments may be made for different sizes of grids and.also for wear on the clamp slides I9I. The arms- I98 and 292 are alsomounted upon the rod I83. The rocker arm .I98 is in turn actuated by ariser cam 299 mounted upon the cam shaft 92. As shown in Fig. 20, whenthe cam 299 rotates in\the direction as indicated by the arrow, thefirst raised portion of said cam which comes into contact with the armI98 moves said arm so as to actuate the bell crank I94,

and thus cause the clamp slides I9I to clamp the grid, whereby the backfeed carriage may feed said grid-through the machine. During thisfeeding operation, the clamp slides I9I engage the grid to such anextent that the cutting edges thereof extend about half way through theside wires. The cam 299 is so related to the cam I13 that the slides I99clamp the grid just prior to the release of the grid by the clamps I66of the front feed carriage. After the back feed carriage hassubstantially completed its feeding motion along the machine, the rockerarm I98 comes into contact with a cam face 29I on the cam 209. Thiscauses an additional actuation of the rocker arm I98 which movesthe-clamp slides I9I an additional amount sufficient to shear throughthe side rods, and thus cut off the completed grid. As shown in Fig. 1,the machine may be provided with a trough 258 into which the completedgrids drop and through which they may be 7 removed from the machine. Inorder to prevent the back feed carriage from dropping the severed end ofthe incomplete grid which is being fed toward the back feed carriage, itis provided with a grid-centering guide 292, as shown in Fig. 20.Although this guide does not clamp the grid, it slidably supports thesame during the period of time in which the clamp slides I9l areretracted from the sides of the grid.

When the front feed carriage has completed its feeding travel throughthe machine, the clamp slides I66 are released as described above. Inorder to permit the front feed carriage to be returned to its originalposition, the split nut I63 is released from the lead screw I65 by meansof a spreader 293. This spreader consists of a tongue which extendsbetween the two halves of the split nut, as shown in Fig. 17, and whichwhen rotated spreads the two h'alves of the split nut against the actionof the biasing spring I64.

The spreader 293 is pivoted in the plate I82, andis provided with aspreader arm 294. The spreader 293 is actuated by means of its arm 294from a lever 295 which is pivoted on a shaft 296 carried by shaftbrackets 2| 3 which are mounted on the lower face of the bed plate 3|.The lever 295 is provided with an actuating spring 291 which tends tovrotate the lever 295 so as to actuate the spreader 293 to release thesplit nut I63.- The action of the spring 291 is restrained by means of apush rod 298 which is'slidably supported on the bed plate 3|. The outerend of the push rod 298 rides upon the closing cam 299 which is likewisecarried on the main cam shaft 92. As the cam 299 rotates in thedirection as indicated by the arrows in Figs. 17 and 19, theend of thepush rod 298 drops off the raised portion of the cam onto its depressedportion, whereupon the actuating spring 291 pulls upon the lever 295 androtates the spreader 293 so as to separate the two halves of the splitnut I63, This action releases the front feed carriage from the leadscrew I65, whereupon the front carriage is ready to be returned to itsinitial position. The cam 299 is so shortly after the clamp slides I66have released the grid. In order to produce relative sliding motionbetween the lever 295 and the spreader arm 294, the lever 295 isprovided with an extension face 2 I2 extending along the machinesufficiently so that the lever 295 is maintained in active e'ngagementwith the arm 294 throughout the travel of the front feed carriage I6Ithrough the machine.

In order to return the front feed carriage to its original position,areturn thrust rod 2I4 is slidably mounted in the rear bearing plateI18, as shown, for example, in Fig. 1. The inner end of the thrust rod2I4 engages the end of one of the outer bearing sleeves I14. The outerend of the'thrust rod 2I4 is provided with a head 2I5 against which arocker arm 2I6 is adapted to push. 'The rocker arm 2I6 is journaled upona stub shaft 2I1 carried by brackets 2I8 mounted upon the bed platesupport 33. The rocker arm 2I6 has pivotally connected thereto a link2I9 which in turn is pivoted to the end of a cam rocker arm 229. The camrocker arm 229 is journaled at its lower end on a stub shaft 292. Rockerarm 229 carries a roller 22I which is adapted to cooperate with a returncam 222 carried by the return cam shaft 223. The return cam shaft iscarried by brackets 293 mounted upon the bed plate support 33. As shownin Fig. 25, the return cam shaft 223 is driven by a right-angled gear224 which engages a right-angled gear 225 mounted upon the main camshaft 92. As the cam shaft 92 rotates and drives the return cam shaft223, the cam 222 pushes upon the roller 6 221, thus rocking the arm 222to the left. This causes the rocker arm 2 I6 to push in against theinner end of the thrust rod 2I4 pushes upon the end of the bearingsleeve I14 which returns the front carriage I62 to its originalposition. Also through the intermediary of the spreading meihher I 8|,the plate I82 carrying the split nut I63 head 2l5 of the thrust rod 2I4,whereupon the rod 209 riding up onto the raised portion of the cam 209,whereupon the lever 205 releases the spreader 203. Due to therelationship between the ends of the split nut I63 and the spreadingmember 203, as shown in Fig. 17, the biasing spring I64 forces thespreading member 203 to rotate back into the position shown in Fig. 17,and also causes the two halves of the split nut I63 to clamp the leadscrew I65, whereupon the front carriage is then again fed along themachine. Just after this action, the clamping members I66 clamp the gridas described above.

After the back feed carriage has completed its feeding and severingaction, as described above, it is released from the lead screw I andreturned to its original position. In order to release the back feedcarriage from the lead screws I65, the split nut I 89 is likewiseprovided with a spreader 226, as shown in Fig. 20. This spreader ismounted on a spreader arm 22'! provided at its end with a roller whichrolls along an extension face 229 of a lever 228. The lever 228 isjournaled on the bearing shaft 206 which, as described above, is carriedby the shaft brackets 2I3. The lever 228 is actuated by a tension spring230 which pulls upon the lever 228 and causes the spreader arm 22'! toactuate the spreader member 226 to separate the two halves of the splitnut I89, and thus release the back carriage from the lead screw I65. Theaction of the actuating spring 230 is normally restrained by the pushrod 23I which is slidably mounted on the bed plate3l. The outer end ofthe push rod 23l rides upon the closing cam 232. When the end of thepush rod 23I is on the raised portion of the cam 232, the split nut ismaintained in its clamping position on the lead screw I65. However, whenthe end of the push rod 23I drops down on the depressed portion of thecam 232, the actuating spring 230 is permitted to come into operation,whereupon the split nut I89 is released from the lead screw I65, asdescribed above. This release occurs just after the clamping members I9Ihave completed their severing operation.

After the split nut I89 has been released from thelead screw I65, theback carriage is returned to its original position by a thrust rod 233which is slidably carried by the rear bearing plate 211, as shown, forexample, in Fig. 1. The inner end of the thrust rod 233 bears againstone end of one of the bearing sleeves 290 while the outer end isprovided with an operating head 234 against which a rocker arm 235 isadapted to push. -The rocker arm-235 is journaled at its lower end onthe stub shaft 2I'I, and is connected by means of a link 236 to the camrocker arm 231. This cam rocker arm is journaled at its lower end on thestub shaft 292. The rocker arm 231 is provided with a roller 238 whichcooperates with a return cam 239 which is mounted upon the return camshaft 223. As the return cam shaft 223 is rotated from the main camshaft 92 through the gears 225 and 224, as described above, the cam 239pushes against the roller 238 and thus actuates the rocker arm 235 whichpushes upon the thrust rod, and thus machine, each carriage clamping thegrid just prior to the release by the other carriage and thusoverlapping in cycle. are fed continuously. Since each carriage needtravel only a distance slightly greater than one- As a result the gridshalf the length of the individual grid, the overall Stripping mechanism.

Before the grids are completed, the loose turns I 249 illustrated inFig. 39 must be removed from the grid. In accordance with present-daypractice, this is usually done after the grids have been removed from'the machine. The present arrangement, however, affords a mechanismwhereby this severing or stripping is accomplished automatically. Inorder to accomplish the stripping, the machine is provided with twoelectrodes 240 mounted as shown in Figs. 17 and 18. The electrodes 240are carried by electrode arms 24I insulated therefrom. The arms 24I arepivotally mounted on the front carriage frame I62, and are provided withextensions 242 which are adapted to contact with the actuating cam 244.Each electrode arm 24I is provided with a biasing spring 243 which urgesthe electrodes The cam 244 is pivotally mounted upon the front carriageframe I62, and is provided with a cam arm 245, the outer end of whichcontacts the actuating pin 246 mounted upon the arm "0 of the bell crankI69. Thus when the arm I10 is actuated so as to clamp the grid betweenthe clamp slides I66, the electrodes 240 are brought into contact withthe grid, as will be more clearly pointed out in connection with Fig.39. As shown in this figure, each grid consists of a series of normalturns 241 swedged at points 248 to the side wires 42 and 43. Between thenormal turns 241 are wounda few loose turns 249. The electrodes 240contact with the first and last loose turn at a point very near therespective side wire 42 or 43. The machine itself is grounded, asindicated at 250. Each electrode 240 is also provided with a conductor25I which leads through a transformer secondary 252 to a ground 253.Each secondary 252 is also provided with a primary winding 254 connectedby means of a main. switch 25I-to some suitable source of alternatingcurrent. Each primary 254 is controlled by a switch 255. After theelectrodes-240 have come into contact with the loose turns of the grid,the switches 255 are closed, whereupon the primary and secondarywindings 254 and 252 are energized. Upon the energization of thesecondary windings, current passes from each electrode 240 through ashort length of winding wire to one of the side rods. The currentpassing through this small portion of the winding wire burns it away,and thus it leaves it disconnected from the tight portion of the woundgrid. This leaves all of the loose turns 249 free so that when the gridis severed, as pointed out above, these loose turns will fall off. Ihave found that the voltage of the secondary windings 252 may be betweenthree and ten volts, five volts being a good working average for mostkinds of wire. Of

course it is to be understood that during this action the switch 251 isin its closed position.

In order to actuate the switches 255 at the proper time, these switchesare mounted upon the bed plate 3|, as shown in Fig. 7, and are eachclosed by means of a switch cam 256 mounted upon the cam shaft 92. Thus,by orienting the cam 256 upon the cam shaft 92, the closure of theswitches 255 takes place at the proper time, that is, shortly after theelectrodes 240 have come into contact with the loose turns of the grid.

Driving mechanism As previously pointed out, the driving mechanism forthe cam shaft 92 constitutes a special feature of this invention. Inorder to drive the cam shaft, as shown in Fig. 2, the drive shaft 16carries a gear 259 which engages a gear 260 mounted upon the back shaft26I which extends throughout the length of the machine and thus iscarried by the support standards 34 and 35 and the bearing plates I11.and I18. The opposite end of the back shaft extends through thestationary bearing 261, as shown in Figs. 1 and 5. As shown in Figs. '23and 24, at the opposite end of the machine from the gear 260, the backshaft carries the epicyclic gear train pinion plate 262. This plate hasmounted thereon to one side thereof, the pinion gear 263. This piniongear meshes with a gear 264 rotatably mounted upon the stationarybearing 261, as shown in Figs. 1 and 5. N on-rotatably mounted upon thestationary bearing 261 is a stationary gear. 265 differing from gear 264by one tooth. The gears 264 and 265 are of the same diameter. The gear263 also meshes withthe stationary gear 265. Due to the fact that thegears 264 and 265 differ from each other by one tooth, as the back shaft26I is rotated, the gear 264 is advanced one tooth for each rotation ofsaid back shaft. Connected to the gear 264 and floating on the backshaft and stationary bearing 261 is the floating sleeve 266,

which at its inner end carries a gear 268 having the same number ofteeth as 264. Thus the gear 268 rotates in synchronism with-the gear264. As shown in Figs. 23 and 24, an intermediate gear 269 meshes withthe gear 268, The'gear 269 is mounted -upon an arm 210 which is swiveledabout the shaft 2,6I as a center. The arm 210 is provided with anadjustment link 21I which is provided with an elongated slot throughwhich passes a lock bolt 212 carried by the support 33. Thus the gear269 may be moved to a limited ex tent around the back shaft 26I andlocked in its adjusted position by means of the lock bolt 212. Meshingwith the intermediate gear 269 is the main cam shaft change gear 213which is rigidly mounted upon the main cam shaft 92. The adjustment ofthe intermediate gear 269, described above, is necessary to take care ofvarious sizes of the change gear 213.

As pointed out above, the winding head I04 is driven fromthe drive shaft16 which also drives the back shaft 26I. The gear ratios are so adjustedthat the winding head I04 makes one complete revolution for eachrevolution of the back shaft 26I'. However, the main cam shaft 92determines the formation of individual grids; that is, during eachcomplete revolution of the cam shaft 92, a complete grid is formed. Thenumber -of turns of winding wire in a complete grid is thereforedetermined by the number of revolutions which the winding head I04 makesfor each revolution of the cam shaft 92. The driving mechanism for thecam shaft described above affords a particularly flexible and simplecontrol for the number of turns in each complete grid. Since, as hasbeen pointed out above, the gear 264, and consequently the gear 268,advance one tooth for each revolution of the back shaft 26I, said gears264 and 268 will also advance one tooth for each revolution of thewinding head I04. Since the gear 268 through the intermediary of thegear 269 drives the cam shaft 92, the number of revolutions which thewinding head or the back shaft 26I makes for each revolution of the camshaft 92 will be determined by the number of teeth in the main cam shaftchange gear 213. Thus, simply by selecting a change gear of a certainnumber of teeth, the grid will have that number of turns. Therefore, bymy arrangement, the number of turns in the grid may be determined by avery rapid and simple adjustment of the machine. In order to permitadjustment of the position of various parts of the machine, when it isnot being driven, the back shaft 26I is provided with a hand wheel 21I.

As pointed out above, the drive of the lead screw I also constitutes aspecial feature of this invention. In order to drive the lead screw I65,the back shaft 26I, as shown in Figs. 5 and 12, is provided with a gear215. This gear, asshown in Fig. 24, meshes with an intermediate gear 216which is carried on an arm 211 swiveled about the back shaft 26I as acenter. The arm 216 is also provided with an adjustment link 218 havingan elongated slot through which passes a lock-down bolt 219 received inthe support 33. Therefore, the position of the intermediate gear 216around the back shaft 26I can be adjusted and said gear can be locked inits adjusted position by means of the lock bolt 219. The lead screw I65is provided with a lead screw change gear 280 which is engaged by theintermediate gear 216.

This results in the fact that the gear 280 advances one tooth for eachtooth on the gear 215. By replacing the gear 280 with other size gears,a very fine adjustment of the speed of travel of the lead screw I65 canbe secured. The adjustment of the gear 216 is necessary in orderto takecare of various sizes of the gear 280.

Winding spool replacement In order to replace the. winding wire spool98, the assembly carrying the swedges and hammers is mounted so as torotate out of place in front of the winding head, whereupon the windingwire spool may he slipped off the pins I 00 and replaced by a fullspool.

As shown most clearlyin Fig. 15, in order to accomplish this rotation,the swedge assembly frame I50 is pivoted on a pivotpin 28I mounted inthe swedge assembly support standard 282, which 'in turn is carried bythe bed plate 3|. The swedge assembly frame I50 is normally locked inposition by means of a locking handle 284 pivoted at one end thereof onthe swedge assembly frame I 50. The locking handle normally locks behinda plate 283 which is mounted upon the swedge support standard 282.

If it is desired to release the swedge assembly from in front of thewinding head, it is merely necessary to raise the outer end of thelocking handle 284, whereupon the swedge assembly frame may be rotatedout of position. Inasmuch as all of the drive for the swedges and thehammers occurs through impact members rather than through any directconnection, this rotation can be accomplished without disturbing thedriving members.

Retersal of grid winding In some instances it may be desirable toreverse the direction in whichthe winding wire iswhich drives thewinding head and also with the gear H2 which. is mounted on the driveshaft 16. The gear H2 is provided with a set screw 285 so that it may beslid along the drive shaft 16 for a limited distance and set in itsadjusted position. Normally the gear 281 is removed from the stub shaft286 and the gear H2 meshes with the gear I01 to drive said gear andwinding head directly as discussed above in connection with the normaldrive of the winding head. To accomplish the reversal of winding, thegear 281 is mounted on the stub shaft 286 and the gear H2 is slid outalong the drive shaft 16 so that it is no longer in direct engagementwith the gear 101, In this position the drive shaft 16 drives the gearI01 8 through the intermediary of the gears H2 and 281, respectively.Under these conditions the gear ill! will be driven in the reversedirection from that in which it was driven directly by the gear H2.

This invention is not limited to the particular details of constructionas described above, as many equivalents will suggest themselves to thoseskilled in the art. For example, grids of the type having but a singleside rod could be made upon such a machine, in which case but a singlecut-' ter, swedge and hammer need be employed. It is accordingly desiredthat the appended claims be given a broad interpretation commensuratewith the scope. of the invention within the art.

What is claimed is: v 1. In a grid-making machine, a substantiallystationary' windingarbor having a supporting surface to support a siderod upon which a winding wire is to be wound to form a grid, cuttingmeans for cutting notches in said side rod, 'into which notches saidwinding wire is adapted to be laid, swedging means for swedging said rodupon said winding wire, and means for moving said cutting and swedgingmeans into engagement with said side rod to deliver cutting and swedgingstrokes respectively to said rod, said cutting and swedging means beingmounted to move in a direction to deliver the force of said cutting andswedging strokes along a llne'passing substantially through the centerof said side rod.

2. In a grid-making machine, a substantially stationary winding arborhaving a pairof supporting surfaces at opposite sides thereof, each tosupport a side-rod upon which awinding wire is to be wound to form agrid, cutting means for cutting notches in said side rods, into whichnotches said winding wire is adaptedt'o be laid, swedging means forswedging said rods upon said winding wire, and means for moving saidcutting and swedging means into engagement with said side rod to delivercutting and swedging strokes respectively to said side rods, saidlast-named means normally moving said cutting and swedg ing means in adirection to deliver the force of said cutting and swedging strokesalong a line passing substantially through the center of the associatedside rod.

3. In a grid-making machine, a substantially stationary winding arborhaving a pair of supporting surfaces at opposite sides thereof, each tosupport a side rod upon which awinding wire is to be wound to form agrid, cutting means for cutting notches in said side rods, into whichnotches said winding wire is adapted to be laid, a pair of swedges forswedging said rods upon said winding wire, means for moving saidcuttingmeans to deliver cutting strokes to said side rods, and means for movingsaid swedgesto deliver swedging strokes to said side rods, both of saidlast-named means normally moving said cutting means and swedges in adirection to deliver the force of said cutting and swedging strokesalong a line passing substantially through the center of the associatedside rod. r

4. In a grid-making" machine, a winding ar bor, having a supportingsurface to support a side rod upon which a winding wire is to .be woundto 'form a. grid, a cutterforcutting notches in said side rod into whichnotches said winding wire is adapted to be laid, a swedge for swedgingsaid rod upon said winding wire, means for causing said cutter andswedge to deliver cutting and swedging strokes respectively to said siderod, and holding means adapted to engage said side rod at a pointadjacent to the point at which said swedge 'comes into contact with saidsiderod, said holding means holding said side rod in intimate contactwith the supporting surface of ing wire around an elongated side rodwire to form a .grid, feeding means for advancing said side rod withsaid winding wire thereon through said machine, cutting means forcutting notches in said side rod, intowhich notches said winding, wireis adapted to be laid, swedging means for swedging said rod upon saidwinding wire, means for moving said cutting and swedging means into Yengagement with said side rod todeliver cut ting and swedging strokesrespectively to said side. rod, said strokes tending to'bend said side,

rod out of a straight line, and means for bending said side rod in adirection reverse to that of the bend due to said cutting and swedgingmeans an amount suflicient to cause said side rod to be straight.

6. Ina grid-making machine, a grid-forming mechanism adapted to wind andsecure a winding wire around an elongatedside rod wire to formsuccessive grids, feeding means for continuously advancing said side rodwith said winding wire thereon through said machine, a cutter forcutting notches in said side rod into which notches said winding wire isadapted to be laid, a swedge for swedging said rod upon said windingwire, means for causing said I cutter and swedge to deliver cutting andswedging strokes respectively to said side rod, said strokes tend-- ingto bend said side rod out 'of a straight line, and means operatingduring'the continuous feeding of said side rod for bending said side rodin a direction reverse to that of the bend due to,

cause said side rod to be straight.

having a supporting surface to support a side rod upon which a windingwire is to be wound to form a grid, a cutter for cutting notches in saidside rod into which notches said winding wire is adapted to be laid, aswedge for swedging said rod upon said winding wire, means for causingsaid cutter and swedge to deliver cutting and swedging strokesrespectively to said side rod, said strokes tending to bend said siderod out of a straight line, and a straightening member for deliveringstraightening strokes to said side rod after the cutting and swedgingthereof, wherebysa'id side rod in the completed grid is straight.

'8. In a grid-making machine, a winding arbor having a supportingsurface to'supportqa side rod upon which a winding wire is to be woundto form a grid, a cutter for cutting notches in said side rod into whichnotches said winding wire is adapted to be laid, a swedge for swedgingsaid for delivering straightening strokes to said side rod after thecutting and swedging thereof, said straightening member being adapted tocontact said side rod and hold it in intimate contact with thesupporting surface of said arbor during swedging.

9. In a grid-making machine, a winding arbor having a supporting surfaceto support a side rod upon which a winding wire is to be wound to form agrid, a cutter for cutting notches in said side rod into. which notchessaid winding wire is adapted to be laid, a swedge for swedging said rodupon said winding wire, means for causing said cutter and swedge todeliver cutting'and swedging strokes respectively to said side rod, saidmeans normally moving said cutter and swedge in adirection to deliverthe force of said' cutting and swedging strokes along a line passingsubstantially through the center of said side rod, said strokes tendingto bend said side rod out of a straight line, a straightening member fordelivering straightening strokes to said side rod after the cutting andswedging thereof, and means for moving said straightening member in adirection to deliver the force of its straightening blows along a linepassing substantially through the center of said side rod.

10. In a grid-making machine, a Winding ar-' bor having a supportingsurface to support a side rod upon which a winding wire is to be woundto form a grid, a cutter for cutting notches in said side rod into whichnotches said winding wire is adapted to be laid, a swedge for swedgingsaid rod upon said winding wire, means for causing said cutter andswedge to deliver cutting and swedging strokes respectively to said siderod, said means normally movingsaid cutter and swedge in a direction todeliver the force of each of said cutting and swedging strokes along aline passing substantially through the center of said side rod, andmeans for adjusting said swedge transversely with respect to said siderod to shift the direction of the force of the swedging strokes throughsaid'side rod to one side of the center of said side rod.

11. In a grid-making machine, a winding arbor having a supportingsurface to support a side rod upon which a winding wire is to be woundto form a grid, a cutter for cutting notches in said 7. In a grid-makingmachine, a winding arbor side rod into which notches said winding wireis adapted to be laid, a swedge for swedging said rod upon said windingwire, means for causing' said cutter and swedge to deliver cutting andswedging strokes respectively to said side rod; said means normallymoving said cutter and swedge in a direction to deliver the force ofeach of said cutting and swedging strokes along a line passingsubstantially through the center of said side rod, said strokes tendingto bend said side rod out of a straight line, a straightening member fordelivering straightening strokes to said side rod after the cutting andswedging thereof, means for moving said straightening member in adirection to deliver the force of its straightening strokes along astraight line passing substantially through the center of said side rod,and means for adjusting said swedge and straightening membertransversely with respect to said side rod to shift the direction of theforce of the swedging and straightening strokes through said side rod toone side of the center of said side rod.

12. In a grid-making machine, a winding arbor having a supportingsurface to support a side rod upon which a winding wire is to be woundto form a grid, a cutter for cutting notches in said side rod into whichnotches said winding wire is adapted to be laid, a swedge for swedgingsaid rod upon said winding wire, means for causing said cutter andswedge to deliver cutting and swedging strokes respectively to said sidered, said means normally moving said cutter and swedge in a direction todeliver the force of each member for delivering straightening strokes tosaid side rod after the cutting and swedging thereof, means for movingsaid straightening member in a direction to deliver the force of itsstraightening blows along a line passing substantially through thecenter of said side rod, means for adjusting said swedge andstraightening member transversely with respect to said side rod to shiftthe direction of the force of the swedging and straightening strokesthrough said side rod to one side of the center of said; side rod, andmeans for adjusting said straightening member longitudinally along saidside rod with respect to said swedge.

13. In a grid-making machine, a winding arbor having a supportingsurface to support a side rod upon which a winding wire is to be woundto form a grid, a cutter for cutting notches in said side rod into whichnotches said winding wire is adapted to be laid, a swedge for swedgingsaid rod upon said winding wire, winding means for carrying the windingwire around said side rod and winding said wire upon said side rod,feeding means for advancing said side rod with said winding ,wirethereon through said machine. and means for deactivating said cutter andswedge during predetermined intervals to prevent said cutter and swedgefrom contacting said side rod during said intervals, whereby the turnsof said winding wire wound on said side rod during said intervals areleft loose.

14. In a grid-making machine, a grid-forming mechanism adapted to windand secure a winding wire around an elongated side rod wire to formsuccessive grids, two feeding members for feeding said side rod throughsaid grid-forming mechanism, said feeding members being con-

